EP0933567B1 - Dichtungsanordnung - Google Patents

Dichtungsanordnung Download PDF

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Publication number
EP0933567B1
EP0933567B1 EP99300090A EP99300090A EP0933567B1 EP 0933567 B1 EP0933567 B1 EP 0933567B1 EP 99300090 A EP99300090 A EP 99300090A EP 99300090 A EP99300090 A EP 99300090A EP 0933567 B1 EP0933567 B1 EP 0933567B1
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EP
European Patent Office
Prior art keywords
strips
seal
strip
carrier
length
Prior art date
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Expired - Lifetime
Application number
EP99300090A
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English (en)
French (fr)
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EP0933567B2 (de
EP0933567A3 (de
EP0933567A2 (de
Inventor
Christopher Wright
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Rolls Royce PLC
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Rolls Royce PLC
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Application filed by Rolls Royce PLC filed Critical Rolls Royce PLC
Publication of EP0933567A2 publication Critical patent/EP0933567A2/de
Publication of EP0933567A3 publication Critical patent/EP0933567A3/de
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Publication of EP0933567B1 publication Critical patent/EP0933567B1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3284—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings characterised by their structure; Selection of materials
    • F16J15/3292—Lamellar structures

Definitions

  • the present invention relates generally to a seal arrangement and in particular to improvements to leaf seals.
  • seals are often required to seal between a rotatable shaft and a housing surrounding the shaft, the housing having a bore through which the shaft extends.
  • a brush seal One type of seal that has been developed for shafts that rotate at relatively high speeds, as found in gas turbine engines, is a brush seal.
  • a plurality of fine bristles such as bronze or stainless steel wire
  • the tips of the bristles wipe against the shaft so as to effect a seal thereagainst.
  • a problem with such brush seals is that in use the bristles tend to flex in an axial, sealing direction, away from the high pressure side of the seal towards the low pressure side. Bending of the bristles in this way reduces the effective radial length of the bristles and so reduces the contact between the bristle tips and the shaft. In turn this reduces the sealing efficiency. Additionally flexing of the bristles can clamp the bristles against each other and against a backing member of the seal. Friction between the bristles and the backing member stiffens the bristles and prevents free movement of the bristles so that they no longer follow the shaft. Excursions of the rotating shaft are therefore not accommodated by the bristles. This leads to clearance gaps opening up between the bristle tips and shaft, and at the other extreme increased wear of the bristles, both of which reduce the seal performance.
  • Leaf seals which are sometimes called foil seals, comprise a number of thin resilient yet flexible strips which are densely packed together with the strips substantially aligned in the sealing direction. One end of the strips is held within a housing whilst the other, distil end of the strip extends across the seal gap and rests on the shaft.
  • Such a seal design is described in European Patent Application EP 0,391,676.
  • the seal elements, comprising the resilient strips in this type of seal are axially stiff and do not tend to bend in the axial, sealing, direction. This type of seal thereby alleviates some of the problems described above in relation to brush seals.
  • US patent No. 5031922 discloses a variant of the brush seal, called a finger seal.
  • the sealing member comprises at least two pairs of annular diaphragm members, each divided by narrow, angled slots into a plurality of radially extending fingers.
  • the fingers will bend in use in just the same way that the bristles of brush seals bend (as outlined in the fifth paragraph, above).
  • the diaphragm members are mounted closely together and provided with a backing ring. Despite this, the fingers will still tend to lock against the backing ring, with the same detrimental effects as in brush seals.
  • the problem that the present invention solves is the provision of a seal arrangement that provides the flexibility of a brush seal to accommodate radial movement, without the disadvantages of, one the one hand, flexing of the seal elements in the axial direction (which weakens the sealing) or, one the other hand, locking of the seal elements against a backing member (which reduces the flexibility).
  • a seal arrangement for effecting a seal between two components to inhibit a flow of fluid, between the two components, in a sealing direction from an upstream side of the seal to a downstream side of the seal, the downstream side of the seal arranged in use to be at a lower pressure than the upstream side of the seal, the seal comprising a carrier adapted for mounting from one of the components, and a plurality of densely packed resilient strips mounted on the carrier to extend therefrom, each strip having a tip which is adapted to wipe on the other component to effect a seal thereagainst in the sealing direction, characterised in that the main surfaces of the strips are arranged substantially parallel to the sealing direction, and there is provided a gap between the main surfaces of adjacent strips, at least at the tip portions of the strips, to allow the tip portions of the strips to move relative to each other and so maintain in operation a flexible seal.
  • the seal is also straightforward to manufacture and is relatively cheap to produce.
  • one component is a rotatable shaft and the other component is a stationary housing.
  • the strips are tapered such that the thickness at the tip of each strip which is arranged to wipe against the other component is less than the thickness at the end portion of the strips that is mounted on the carrier.
  • each strip may be a step change reduction in the thickness of the strip.
  • the thickness of each strip may preferably be reduced in a series of steps along the length of the strip towards its tip.
  • a spacer strip may be interposed between adjacent strips there may be provided a spacer strip, the spacer strip extends from the carrier and is of a shorter length than the strips thereby providing a gap between the tips of the strips.
  • the strips Preferably when viewed in the sealing direction the strips extend from the carrier at an angle to a direction perpendicular to the carrier.
  • the strip may be bent part way along its length such that the strip is divided into two portions, first portion that is mounted on and extends from the carrier, and a second portion which extends from the first portion and is arranged to wipe against the other component, the second portion extending at an angle to the first portion. Furthermore the strips may be bent at a plurality of positions along their length such that the strips are divided into a plurality of portions, each portion extending at a different angle to the other portion of the strip. The strips may be curved in the direction of the length of the strips extending from the carrier to the tips of the strips that are arranged to wipe against the other component.
  • Bending, or curving the individual strips of the seal provides an improved method of ensuring that there is a gap between individual strips whilst allowing the strips to abut each other at the other end.
  • the overall leakage through the seal is reduced.
  • Bending of the strips to control the gap between strips is also simpler to manufacture than radially tapering the thickness of the strips.
  • the individual strips, since they abut at one end, can also be simply and easily assembled and fixed in position by welding or other means.
  • the strips are mounted with the width of the strips at an angle to the sealing direction of the seal.
  • the seal may be provided with a damper which acts on the strips to damp relative movement of the tips of the strips which are arranged to wipe against the other component.
  • the damper comprises a front skirt and back skirt which extend from the carrier on opposite sides of the strips, the front and back skirts are separated from the edges of the strips by a gap and enclose a substantial portion of the strips therebetween such that, in use, viscous damping of the strips is produced.
  • the damper may comprise at least one finger member that extends from the carrier, the tip of the finger member touches and is urged against one of the edges of a plurality of the strips part way along the length of the strips.
  • the damper may comprise a damping member which is suspended from the carrier by a plurality of wires and rests against one edge of a plurality of the strips part way along the length of the strips, the damping member adapted in use to be urged against the edge of the strips by a leakage flow though the seal.
  • the seal may also comprise a second plurality of densely packed resilient strips arranged substantially parallel to the sealing direction and mounted on the carrier to extend therefrom, with the tips of each strip adapted to wipe on the other component to effect a further seal thereagainst, the second plurality of strips mounted, in a sealing direction, in flow series relationship with the first plurality of strips.
  • the second plurality of strips may be arranged such that when viewed in a sealing direction the gaps between adjacent strips are substantially obscured by the strips of the second plurality of strips.
  • the gap between adjacent strips is less than 20% the thickness of the individual strips.
  • the seal is adapted for use in a gas turbine engine.
  • Figure 1 shows a seal assembly for sealing a clearance gap C between a shaft 2, rotating about an axis 3, and a stationary housing 4, such as may be found in, for example, a gas turbine engine.
  • the seal assembly prevents or restricts a flow of fluid, for example high pressure air, in a sealing direction (shown by arrow 22) from a region 24 of relatively high pressure to a region 26 of lower pressure.
  • the shaft 2 rotates within a inner bore in a housing 4 through which the shaft 2 extends.
  • the seal assembly comprises a plurality of relatively thin resilient seal strips 6 which are sandwiched between a carrier 13 comprising an annular front plate 8 and an annular backplate 10. The strips 6, front plate 8 and backplate 10 may all welded together around an outer circumference to form a seal unit 12.
  • the seal unit 12 is mounted within a counter bore 14, in the housing 4, by a circlip 16 which is sprung into a groove 18 within the housing 4. It will be appreciated though that the seal unit could be retained by other means which may also be incorporated with the means for retaining the front plate 8, backplate 10, and strips 6 together as a seal unit 12.
  • the seal strips 6 are densely packed around the circumference of the shaft 2 and extend in a generally radial direction such that their free distil ends 20 wipe against the outer circumference of the shaft 2, as is shown in figure 2. As will be appreciated from figure 2 the strips 6 extend at an angle ⁇ to the true radial direction 28 of the seal such that they trail the direction of rotation (shown by arrow X)of the shaft 2. Typically an angle ⁇ between 20° and 70° is used. However they can extend radially (i.e. at an angle of 0°) or at any other angle.
  • the seal strips 6 are arranged edge on within the seal assembly such that the width W of the strip 6 lies generally in the sealing direction 22.
  • the sealing direction 22 in the embodiment shown is generally parallel to the axis 3 of the shaft 2 and seal.
  • the width W of the strip 6 is greater than the thickness t of the strip 6 in order to provide adequate stiffness in the sealing (axial) direction 22. Consequently the strips 6 exhibit a high degree of resistance to bending in the seal direction 22 alleviating some of the problems found in brush seals caused by bending of the bristles against the backing members.
  • the thickness t of the strips 6 is similar to the bristle diameter in a brush seal. Typically this about 0.5mm.
  • the strips 6 are also made from similar materials as are used to make the bristles in brush seals. Typically the strips 6 are made from stainless steel or other high temperature materials such as for example Haynes 25, INCO 718 or Nimonic.
  • each strip 6 is essentially flat and planar and lies with its plane parallel to the sealing direction 22.
  • each strip 6 could lie with its plane at an angle ⁇ to the sealing direction 22 as shown in figure 6b.
  • Yet another possibility is for each strip 6 to be curved across its width W, although this is not shown.
  • the seal is generally similar to the seal described in EP 0,391,676. However as shown in figure 2 at the point where the strips 6 wipe against the shaft 2 the strips 6 are separated from each other by a small discrete gap 30. This gap allows a degree of circumferential movement and bending of the strips 6 before they abut each other and produce an effectively solid seal.
  • the seal is therefore compliant and resilient in a radial direction whilst being relatively stiff in a sealing (axial) direction 22. Circumferential movement of the strips 6 reduces the effective radial length thereof and moves the tip 20 of the strip 6 radially outwards. Consequently by circumferential bending of the strips 6 the seal can accommodate a degree of relative radial movement of the shaft 2 without becoming effectively solid.
  • Radial movement of the shaft 2 relative to the housing 4 and the seal can occur in particular when such seals are used within gas turbine engines.
  • the relative movement of the shaft 2 can be caused by a number of factors including for example thermal growth of the shaft 2, slight eccentricities in mounting and aligning of the shaft 2 relative to the housing 4 causing the shaft 2 to orbit, and uneven transient loading of the shaft 2.
  • the gap 30 between adjacent strips 6 is sized to accommodate the expected relative radial movement of the shaft 2 such that the strips 6 are free to move circumferentially, in response to the expected radial movement of the shaft 2, without the tips 20 of the strips 6 which wipe against the shaft 2 abutting each other.
  • the inter strip gaps 30 it is important that the inter strip gaps are not excessive, or greater than the minimum required.
  • the size of the gap 30 is approximately less than 20% of the thickness t of the strips 6.
  • the required gap 30 between adjacent strips 6 can be provided by a number of alternative arrangements. As shown in figure 2 the gap 30 between the tips 20 of adjacent strips 6 is achieved by reducing the thickness t of the radially inner ends 32 of the strips 6. The thickness t of the strips 6 being reduced by for example etching the end portions 32 of the strips 6 in a suitable etchant to remove a portion of material from the end portion 32 of the strip 6. The thickness t of the strip 6 could however be reduced gradually in stages as shown in figure 3. A yet further possibility (not shown) is to gradually taper the strip 6 in a radial direction.
  • FIG. 4 Another arrangement for providing a gap 30 between adjacent strips 6 is shown in figure 4.
  • individual strips 6d of a substantially constant thickness are separated from each other by spacing strips 7.
  • the spacing strips 7 are of a shorter radial length and extend from the housing 4. The free ends of the spacing strips end radially part way along the length of the strips 6d. Successive strips 6d are therefore separated from each other by the thickness t 1 of the spacing strips 7, thereby providing a gap 30 between the tips 20 of the strips 6d.
  • only one spacing strip 7 has been shown in figure 4 it will be appreciated that multiple spacing strips 7 of varying radial length could be used between successive seal strips 6d.
  • the effective gap 30 provided between the strips 6d being similar to that shown in figure 3.
  • the outer portions 36 of the strips 6 are therefore densely packed, essentially solidly in this radially outer region. This ensures that the strips 6 are aligned and positioned within the seal. It also simplifies the manufacture of the seal allowing the strips 6 to be easily welded together. Furthermore since there is no gap between the outer portions 36 of the strips 6 in this region, leakage through the seal, between the strips 6 is reduced.
  • the tapering of the strips 6 required to produce a gap 30 at the tips 20 of the strips 6 should take into account the reduction in circumferential space available between the outer and inner radii. If the tapering is not sufficient then any gap 30 between strips 6 would tend to close up and reduce towards the radially inner end. It being essential according to the invention that a sufficient gap 30 is provided at the tips 20 of the strips 6. Preferably the tapering should be such that the gap 30 increases towards the tip 20 of the strips 6, as shown in figure 3. The most space being required at the tips 20 of the strips 6 to allow a given degree of circumferential movement of the strips 6.
  • FIG. 5a A further embodiment is shown in figure 5a.
  • the seal is generally similar to the above described seals except that the plurality of radially extending strips 6b which comprise the seal are bent part way along their radial length. The general arrangement of this seal will therefore not be described further.
  • the bent strips 6b extend from the carrier 13 and housing 4 such that a first portion 38 of the strip is at a first angle ⁇ to the true radius 28 of the seal, whilst a second portion 40 of the strip 6b is at a second angle ⁇ to the true radius 28 of the seal.
  • the first portion 38 of the strips 6b abut each other and ensure that the strips 6b are correctly aligned and allow simple assembly of the seal. This is similar to the way that the radially outer portions 36 of the tapered strips 6 are arranged.
  • the strips 6b are arranged within the seal such that the point of inflection 42 of each of the strips 6b lies on a circle concentric 44 with the seal.
  • the point of inflection 42 of each strip 6b is overlapped by the first portion 38 of an adjacent strip 6b thereby providing a small discrete gap 30 between successive strips 6b.
  • FIG. 5b A variation on the arrangement shown in figure 5a is shown in figure 5b.
  • each of the individual strips 6c making up the seal is bent at a number of inflection points 44a,44b,44c along its length to produce a multi-bend strip 6c.
  • These multi-bend strips 6c are assembled in a similar way to the single bend strip 6b arrangement described above, such that the points of inflection 44a,44b,44c of the strips 6c lie on a series of concentric circles 46a,46b,46c about the seal, with each adjacent strip 6c slightly overlapping each point of inflection 44a,44b,44c of a previous strip 6c.
  • Different portions 48,50,52,54 of the strips 6c extend from the housing at different angles ⁇ , ⁇ , ⁇ , ⁇ to the true radius 28 of the seal.
  • a small discrete gap 30 between successive strips 6c is thereby provided allowing the tips 20 of the strips 6c to move circumferentially to accommodate any radial movement of the shaft 2 into the seal.
  • An advantage of this multi-bend arrangement is that the gap 30 between the strips 6c can be more accurately controlled and varied along the length of the strip 6c.
  • the size of the gap 30 and its variation along the length of the strips 6c being determined by the number of bends 44a,44b,44c in the strips 6c and the bend angle ⁇ , ⁇ , ⁇ , ⁇ .
  • the gap 30 can therefore be minimised along the length of the strips 6c, reducing leakage through the seal whilst still providing sufficient space, particularly at the tip 20, for the strips 6c to move.
  • the size of the gap 30 required to allow the strips 6c to move the required degree varies along the length of the strips 6c.
  • a larger gap 30 being required between the radially inner ends of the strips 6c than is required at the radially outer ends to allow the same degree of movement of the strips 6c.
  • the multi-bend arrangement can be further developed and improved by using radially curved strips of for example circular, ellipsoid or parabolic shape as shown in figure 5c.
  • the exact shape of the strips being determined by the shape and size of the gap required to allow the desired movement of the strips.
  • the use of such curved strips allows even greater control of the size of the gap between strips over the length of the strip. Leakage through the seal can therefore be further minimised.
  • seals have a leakage flow rate that is dictated by the inter strip gap 30.
  • two seal elements 56,58 can be used in tandem, one behind the other, in the sealing direction 22 as shown in figure 8.
  • Each of the two seal elements 56,58 comprises a similar arrangement of radially extending strips 6 which circumferentially surround the shaft 2.
  • the downstream seal element 58 is separated from the upstream seal element 56 by a small clearance 60.
  • the strips 6 in each element 56,58 are therefore free to move independently.
  • the downstream element 58 is also rotated a small degree such that the seal strips 6 of the downstream seal element 58 overlap the gap 30 between adjacent strips 6 of the upstream seal element 56 when viewed in the sealing(in this embodiment axial) direction 22.
  • the strips 6,6a,6b,6c,6d are separated from each other by a discrete gap 30 they are free to move. This can give rise to, or exacerbate, vibration or flutter of the strips 6,6a,6b,6c,6d. Such vibration or flutter is undesirable since it can over time cause damage to the strips 6,6a,6b,6c,6d. Consequently it may be necessary to provide the seal with means to damp or reduce the vibration or flutter of the strips 6,6a,6b,6c,6d.
  • one method is to configure the front 8' and back plate 10' of the seal such that they extend over the majority of the radial length of the strips 6.
  • the front 8' and back plate 10' are spaced from the strips 6 by only a small gap 62.
  • the front 8' and back plate 10' thereby form skirts which enclose a significant part of the strips 6 allowing viscous effects of the narrow inter strip gaps 30 to dampen any vibration or flutter.
  • Extended front 8' and back 10' plates which extend to near the other component 2, also improve the seal performance since the plates 8', 10' provide a physical barrier to the leakage flow, further restricting leakage through the seal.
  • the plates 8',10' also help prevent dirt or other material from being entrained into the seal and possibly clogging the inter strip gaps 30. For these reasons such extended front and back plates 8',10' may accordingly be used in other embodiments of the invention.
  • a split skirt damper as shown in figure 7b, comprises a number of radially extending fingers 64 which are sprung such that the distil end 66 of the each finger 64 abuts and presses against the upstream front edge 68 of a number of the seal strips 6 of the seal. The friction between the end of the fingers 66 and the edges of the strips 68 will tend to damp the vibration and flutter of the strips 6. The fingers 64 also tend to partially link the strips 6 together since the fingers 64 contact a number of adjacent strips 6.
  • a ring damper is shown in figure 7b and comprises a ring 70 which is loosely mounted concentrically with the shaft 2 by a number of wires 72 such that it rests against the upstream edge 68 of the strips 6.
  • the ring 70 is pressed against the edges 68 of the strips 6 by the leakage flow of fluid in the sealing direction 22 and the pressure differential, between the upstream pressure 24 and downstream pressure 26, across the seal. It thereby damps any vibration in a similar way to the split skirt damper.
  • the strips 6f may also be attached to the rotating component 2 rather than the stationary component 4 such that the strips 6f rotate.
  • the strips 6f can also be arranged to be outward facing, as shown in figure 9, such that they are fixed at their radially inner ends 72 with the radially outer ends 74 of the strips 6f wiping against the other component 4. As with the radially inwardly facing arrangement the curved strips 6f produce an inter strip gap 30 at their free distil ends 74.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Seal Device For Vehicle (AREA)

Claims (19)

  1. Dichtung zur Bewirkung einer Abdichtung zwischen zwei Bauteilen (2, 4) zum Sperren einer Fluidströmung zwischen den beiden Bauteilen (2, 4) in einer Dichtungsrichtung (22) von einer stromaufwärtigen Seite (24) der Dichtung nach einer stromabwärtigen Seite (26) der Dichtung, wobei die stromabwärtige Seite (26) der Dichtung im Betrieb auf einem niedrigeren Druck steht als die stromaufwärtige Seite (24) der Dichtung und die Dichtung einen Träger (12) aufweist, der von einem der Bauteile (4) gelagert wird und eine Vielzahl von dicht gepackten elastischen Streifen (6) im Träger (12) derart festgelegt ist, dass die Streifen aus dem Träger (12) vorstehen und jeder Streifen (6) eine Spitze (20) besitzt, die auf dem anderen Bauteil (2) schleift, um gegenüber diesem Bauteil (2) eine Abdichtung in Dichtungsrichtung (22) zu bewirken,
    dadurch gekennzeichnet, dass die Hauptoberflächen der Streifen (6) im Wesentlichen parallel zur Dichtungsrichtung (22) verlaufen und ein Spalt (30) zwischen den Hauptoberflächen benachbarter Streifen (6) wenigstens im Bereich der Spitzen der Streifen (6) vorgesehen ist, damit die Spitzenabschnitte (20) der Streifen (6) relativ zueinander beweglich sind und so im Betrieb eine flexible Abdichtung aufrecht erhalten.
  2. Dichtung nach Anspruch 1, bei welcher der eine Bauteil (2) eine drehbare Welle und der andere Bauteil (4) ein stationäres Gehäuse ist.
  3. Dichtung nach den Ansprüchen 1 oder 2, bei welcher die Streifen (6) derart verjüngt ausgebildet sind, dass die Dicke (t) der am anderen Bauteil (2) schleifenden Spitze (20) eines jeden Streifens (6) kleiner ist als die Dicke (t) an jenem Endabschnitt des Streifens (6), der im Träger (12) montiert ist.
  4. Dichtung nach einem der vorhergehenden Ansprüche, bei welcher über die Länge eines jeden Streifens (6) nach seiner Spitze (20) hin die Dicke (t) des Streifens (6) in einer Stufe vermindert ist.
  5. Dichtung nach Anspruch 4, bei welcher die Dicke (t) eines jeden Streifens (6) in mehreren Stufen über die Länge des Streifens (6) nach seiner Spitze (20) hin vermindert ist.
  6. Dichtung nach einem der vorhergehenden Ansprüche, bei welcher ein Abstandshalterstreifen (7) zwischen benachbarte Streifen (6d) gefügt ist und dieser Abstandshalterstreifen (7) sich vom Träger (12) aus erstreckt und eine kürzere Länge hat als die Streifen (6a), wodurch ein Spalt (30) zwischen den Spitzen (20) der Streifen (6d) gebildet wird.
  7. Dichtung nach einem der vorhergehenden Ansprüche, bei welcher in Dichtungsrichtung (22) betrachtet die Streifen (6) sich vom Träger (12) unter einem Winkel in einer Richtung senkrecht zum Träger erstrecken.
  8. Dichtung nach einem der vorhergehenden Ansprüche, bei welcher der Streifen (6b) über einen Teil seiner Länge derart abgebogen ist, dass der Streifen in zwei Abschnitte (38, 40) unterteilt wird und der erste Abschnitt (38) am Träger (12) montiert ist und sich von diesem erstreckt, während ein zweiter Abschnitt (40) vom ersten Abschnitt (38) vorsteht und an dem anderen Bauteil (2) schleift, wobei sich der zweite Abschnitt (40) unter einem Winkel gegenüber dem ersten Abschnitt (38) erstreckt.
  9. Dichtung nach Anspruch 8, bei welcher die Streifen (6c) an mehreren Stellen (44a, 44b, 44c) über ihre Länge derart abgebogen sind, dass die Streifen (6c) in mehrere Abschnitte (48, 50, 52, 54) unterteilt werden und jeder Abschnitt (48, 50, 52, 54) sich unter einem anderen Winkel gegenüber dem anderen Abschnitt des Streifens (6c) erstreckt.
  10. Dichtung nach einem der vorhergehenden Ansprüche, bei welcher die Streifen (6e) in Längsrichtung gekrümmt sind und sich vom Träger (12) nach den Spitzen (20) erstrecken, die an dem anderen Bauteil (2) schleifen.
  11. Dichtung nach einem der vorhergehenden Ansprüche, bei welcher die Streifen (6) derart montiert sind, dass sich die Breite (w) der Streifen (6) unter einem Winkel (β) zur Dichtungsrichtung (22) der Dichtung erstreckt.
  12. Dichtung nach einem der vorhergehenden Ansprüche, bei welcher ein Dämpfungsglied (8', 64, 72) vorgesehen ist, das auf die Streifen (6) einwirkt, um eine Relativbewegung der Spitzen (20) der Streifen (6) zu dämpfen, die am anderen Bauteil (2) schleifen.
  13. Dichtung nach Anspruch 12, bei welcher das Dämpfungsglied eine vordere Einfassung (8') und eine hintere Einfassung (10') aufweist, die sich vom Träger (12) auf gegenüberliegenden Seiten der Streifen (6) erstrecken, wobei die vordere Einfassung (8') und die hintere Einfassung (10') von den Rändern der Streifen durch einen Spalt (62) getrennt sind und einen beträchtlichen Teil der Streifen (6) dazwischen derart einschließen, dass im Betrieb eine Viskositätsdämpfung der Streifen (6) erzeugt wird.
  14. Dichtung nach Anspruch 12, bei welcher das Dämpfungsglied (64) wenigstens ein Fingerglied aufweist, das sich vom Träger erstreckt, wobei die Spitze (66) des Fingergliedes einen Rand (68) der Vielzahl der Streifen (6) über einen Teil der Länge der Streifen (6) berührt und dagegen gedrückt wird.
  15. Dichtung nach Anspruch 12, bei welcher das Dämpfungsglied (72) einen Dämpfungskörper (70) aufweist, der vom Träger über mehrere Drähte aufgehängt ist und gegen einen Rand (68) der Vielzahl der Streifen (6) an einer Stelle über die Länge der Streifen (6) anliegt, wobei der Dämpfungskörper im Betrieb gegen den Rand der Streifen durch die durch die Dichtung fließende Leckströmung gedrückt wird.
  16. Dichtung nach einem der vorhergehenden Ansprüche, bei welcher eine zweite Vielzahl (58) von dicht gepackten elastischen Streifen (6) im Wesentlichen parallel zur Dichtungsrichtung (22) angeordnet und an einem Träger (12) montiert ist, um sich von diesem zu erstrecken, wobei die Spitzen (20) eines jeden Streifens (6) auf dem anderen Bauteil (2) schleifen, um eine weitere Dichtung gegenüber diesem Bauteil zu bewirken und wobei die zweite Vielzahl (58) von Streifen (6) in Dichtungsrichtung (22) in Hintereinanderschaltung mit der ersten Vielzahl (56) von Streifen montiert ist.
  17. Dichtung nach Anspruch 16, bei welcher die zweite Vielzahl (58) von Streifen derart angeordnet ist, dass bei Betrachtung in Dichtungsrichtung (22) die Spalte (30) zwischen benachbarten Streifen (6) im Wesentlichen durch die Streifen (6) der zweiten Vielzahl (58) von Streifen abgedeckt sind.
  18. Dichtung nach einem der vorhergehenden Ansprüche, bei welcher der Spalt (30) zwischen benachbarten Streifen kleiner ist als 20% der Dicke (t) der einzelnen Streifen (6).
  19. Gasturbinentriebwerk mit einer Dichtung nach einem der vorhergehenden Ansprüche.
EP99300090A 1998-01-30 1999-01-06 Dichtungsanordnung Expired - Lifetime EP0933567B2 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GBGB9801864.1A GB9801864D0 (en) 1998-01-30 1998-01-30 A seal arrangement
GB9801864 1998-01-30
US09/228,274 US6267381B1 (en) 1998-01-30 1999-01-11 Resilient strip seal arrangement

Publications (4)

Publication Number Publication Date
EP0933567A2 EP0933567A2 (de) 1999-08-04
EP0933567A3 EP0933567A3 (de) 2000-02-23
EP0933567B1 true EP0933567B1 (de) 2006-11-29
EP0933567B2 EP0933567B2 (de) 2011-08-10

Family

ID=26313031

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99300090A Expired - Lifetime EP0933567B2 (de) 1998-01-30 1999-01-06 Dichtungsanordnung

Country Status (3)

Country Link
US (1) US6267381B1 (de)
EP (1) EP0933567B2 (de)
GB (1) GB9801864D0 (de)

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Also Published As

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US6267381B1 (en) 2001-07-31
EP0933567B2 (de) 2011-08-10
EP0933567A3 (de) 2000-02-23
EP0933567A2 (de) 1999-08-04
GB9801864D0 (en) 1998-03-25

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